Elastic-fluid turbine.



No. 739,965. PATENTED SEPT. 29, 1903.

J. WILKINSON.

ELASTIC FLUID TURBINE.

APPLIOATION FILED JUNE 16, 1903.

110' MODEL. 4 SHEETS-SHEET 1 w w w WITNESSES No.739, 965 PATENTBDSEPT.29,1903.

- J. WILKINSON. v S

ELASTIG FLUID TURBINE.

APPLICATION FILED'JUNE 16, 1993. p

N0 MODEL. 4 SHEETB BHEET 2.

WITNESSES: INKENTOI? Wyn/W in: Noam: warns co Pnmo- N a r v v No. 739,965. ,PATENTBD SEPT. 29, 190.

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ELASTIC FLUID TURBINE.

Arruonmzi nun man 16, mos. no MODEL.

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PATENTED SEPT. 29, 1903.

J. WILKINSON. ELASTIC FLUID TURBINE. I

APPLICATION FILED JUNE 16, 1903.

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N0 MODEL.

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' BY I X7 W/TNESSES ATTOH Y Patented September 29,

PATENT OFFICE.

JAMES WILKINSON, or B'IRMINGIiAM, ALABAMA.

ELASTIC-.FLUID TURBINE.

SPECIFICATION forming part of Letters Patent No. 739,965, dated September 29, 1903.

d I Application filed June 16, 1903. Serial No. 161,708. (No model.

To all whom it vmay concern;

Be it known that I, JAMES WILKINSON, a citizen of the United States, residing at Birmingham, in the county of J eiferson and State of Alabama, have invented certain new and useful Improvements in Elastic-Fluid Turbines, of which the following is a specification.

My invention relates to'improvements in elastic-fluid turbines wherein fluid-pressure is converted by stages into velocity or vis viva, which is transformed into mechanicalpower by being directed against successive rows of revolving vanes peripherally mounted on rotor-wheels. 7

According to my invention a plurality of separate compartments are formed within the casing of'the turbine by diaphragm-partitions provided with central openings encircling the main shaft, upon which are mounted a series of rotor-wheels, one of which revolves. within each separate compartment. Nozzles are disposed around the several diaphragms, so that they deliver the fluid stream successively to the vanes carried by the rotor-wheels, and

with the vanes formworking passages, which enlarge in the directionof the flow of the fluid to accommodate the increasing volume of the stream as its pressure is convertedinto velocity and fractionally abstracted This step-by-step or stage expansion of the fluid-pressure, whether effected in acompound turbine, as above described,for in a pluralityof separate casings between which the nozzles are formed as conduits, requires as an essential prerequisite that the pres" sure maintained in the several compartments should be constant; otherwise the turbine parts will be thrown out of proportion to the pressure and a material loss of efficiency will efliciency; but if the chamber-pressure be greater a heterogeneous motion will be set up in the nozzle, which will retard the velocity or vis viva developed therein; It is also true that if the predetermined pressures of the several stages vary there will be a corresponding variation in the volume of the fluid streams, which will'defeat the proportions which should be maintained for a constant speed of rotation between the relatively increasing volume of the streams and the correspondingly enlarged nozzle passages.

This variation in the stage pressure is principally caused by the uncertain element of leakage. It is therefore of prime importance to the successful operation of a turbine adaptedto expand the pressure in stages and fractionally abstract its vis viva, either in a series of separate simple turbines or in a compound turbine, wherein the-stages are in reality complete simple turbines within one shell, that there should be no leakage of the fluid between the wheel-chambers that cannot be accurately calculated, and for the sake of economy there should be none at all. The mostserious difliculty'encountered in controlling or stopping this leakage arises from the great speed attained by the revolving parts of the turbine and their angular adjustmentor vibratory play relative to the stationary parts, which renders any positive ple clearance around the shaft and atthe same time is capable of adapting itself to any and all variations of the rotating parts,

whether transversely,vertically, or angularly. According to my invention I meet these requirements by interposing annular pressurereducing valves at the points of leakage around the shaft between compartments or in the stuffing-boxes and so construct them that the difference between the pressures on either side of the valves is utilized to automatically suspend them out of frictional engagement with or to regulate their approximation to the revolvingdisks orwheels thatform their seats,

with a view to controlling the leakage at these points. \Vithin this valve in the clearancespace between it and the revolving parts a pressure of equilibrium is maintained by the regulated leakage from the higher to the lower pressure, which is intermediate the two pressures and which suspends the valve so that it acts with a wired rawing action against its high-pressure seat to control the leakage. The valve is made free to rock or move longitudinally of the turbine, and since it leaves ample clearance around the shaft it readily and automatically adjusts itself to all variations of the rotatmg parts, and at the same time will so control the leakage that the compartment or stage pressures maybe accurately calculated. Having by these means reduced theheretofore-variableleakagebetweenstages to a point where it can be readily calculated, it is necessary to so construct the nozzles that they will effect the desired drop in pressure at each stage. This drop will be proportioned to the number of stages, ranging from ninety pounds in a single-stage turbine to twenty pounds in a five-stage turbine, considering the boiler-pressure at one hundred pounds. In the former instance the nozzle must convert ninety per cent. of the pressure into velocity, while in the latter the succeeding nozzles must convert, respectively,twenty percent.,twenty-fivepercent.,thirty-threeper cent.,fiftypercent.,andninetypercent.,of the stagepressuresinto velocities. When the dro is below about forty-two per cent. of the pressure,l use nozzles of the converging or straight types, wherein the fluid in passing therethrough expands only in the lineal direction of its flow, but when more than this percentage is to be transformed into velocity I use nozzles of the De Laval type, wherein the fluid expands both liueally and laterally. Thus according to my invention in a compound turbine or series of simple turbines the first row or rows of nozzles maybe converging, the intermediate straight, and the last expanding, which arrangement is of material importance to the successful operation of stage expansion-turbines, for if expanding nozzles were used in the earlierstages the fluid would be expanded below the pressure of the receiving-chamber, which would result in the development of heterogeneous motion in. the fluid stream before the point of efflux, or if a straight nozzle were used at the final stage it would not convert all of the pressure into "elocity, but would permit a portion of-it to escape through the vanes into the exhaust.

It is a further object of my invention to provide valves in the several nozzles and to so connect them up in the direction of the flow of the fluid across the several stages that the corresponding valves in each set are simul-v taneously operated and the turbine regulated uniformly throughout the several stages and its power varied according to the load without altering the relative Volume of the elastic fluid delivered to the several compartments.

the packing-ring for the valve.

My invention consists in the construction and arrangement of parts hereinafter described, and more particularly pointed out in the claims, reference being had to the accompanying drawings, which form a part hereof, and in which- Figure 1 is a sectional view of the turbine, taken through the central line of two sets of oppositely-disposed fluid-passages provided with valves and linked operating-gear-therefor. Fig. 2 is a side view partly broken away to show in section the nozzles, valves, and rotating vanes of a three-stage turbine, with a modified form of valve-operating gear. Fig. 3 is a broken away sectional elevation corresponding to that of Fig. 2, and showing a three-stage turbine in which the valves are omitted, the nozzles of the upper rows being of the straight type with parallel sides,

while the lower nozzles are of the expansion type, which increase in cross sectional area toward their discharge ends. Fig. 4 is a similar view of a four-stage turbine wherein the nozzles are all of the straight. type. Fig. 5 is an enlarged view showing the annular valve and the manner of mounting it within the diaphragms between the rotor-wheels. Figs. 6 and 7 are detail views of the valve. Figs. 8, 9, 10, and 11 show modifications of the valve and illustrate the principle of its action. Figs. 12 and 13 are detail views of Fig. 14 is a plan view of one of the diaphragm-partitions, a vertical section of which is shown in Fig.

15, with views of its several parts in Figs. 10, 117, 18, and 19.

Similar reference-numerals refer to'thc same parts throughout.

According to my invention as applied to a compound turbine the casing is provided with a number of transversely-arranged diaphragm-partitionsl, that divide its interior into transverse chambers through which the turbine-shaft 2 extends, with ample clearance between itself and the centrally-dis posed openings in the partitions within which it revolves. These chambers constitute wheelcompartments, and within each of them rcvolves arotor-Wheel 3, keyed to the shaft and provided with a ring of concavo-convex vanes or blades 4 around its circumference.

The fluid enters the turbine through the circular passage 5 in the head of the casing G and is directed by a series of nozzle-passages 7, formed by a series of inclined partitions, against the revolving vanes in the first compartment. After passing through the nozzles 7 and impinging upon the first ring of vanes 4 the fluid-pressure reaches the second chamber through a similar series of nozzle-passages formed in the diaphragmpartitions around their outer peripheries, and arranged to direct the streams of fluid-pressu-re against the ring of vanes revolving in the second chamber, and so on through the series of wheel-compartments and nozzle-passages until the fluid is delivered by the last wheel to the circular exhaust-passage S' in the head 9, from-which it may be discharged through outlet into the atmosphere or a condenser. Each of the nozzles7 has a wellrounded entrance to keep their capacity efficiency high, and when it is desired to regulate the turbine according to varying loads I provide a separate valve 11, located within and when open forming a part of the rounded entrance or throat of each nozzle. These valves are preferably cylindrical and have a centrally and longitudinally disposed fluidpassage formed with rounded sides 12, which constitute a part of the nozzlethroat when admitting fluid.

The diaphragm-partitions 1 are preferably dished against the pressure to increase their strength to withstand heavy strains and have 1 circumferential shoulders 13 and flanges 14,

which constitute the sides of the turbine-cas-' ing. The nozzle-passages 7 pass'at an incline through the shoulder 13, and seats for the cylindrical valves are bored therein radially from the outside.- Into the entrances of these rounded valve-openings, which-are threaded, are secured the packing-glands 15, through which the stems 16 of these valves pass.- (Jranks 17 on these stemsare linked together in series from one row to another in the direction of the flow of the'fluid by links 18, so that in varying the power of the turbine according tojchanging loads thesame number of nozzles will be thrown on or off through-' out the stages, and-it will be noted that by operating these valves in the direction of the travel of the fluid the streams delivered by those nozzles of the first row which are open will not be deflected fromv a substantially straight course to the exhaust by reason of those nozzles in the succeeding stages in the line of thestreams flow being closed, as might readily occur if the valves were linked together in vertical rows.

For operatingthe valves a crank or handle 19 may be-mounted directly on a valve-stem or, as shown in Fig. 2, on a separate'spindle 20 when a short crank 21 thereonis connected,

by a link 22 withthe links 18, through which the'several valve-cranks are operated. It will'be noted'thatthe, spindle 20 is not in alinement with the valve-stems, but is so disposed relatively to cranks 17 that when the valves are closed the links 18 and 22 will" be in alinement with crank 21, which latter will be on the dead-center,'as it were. the eflect of retarding the movement of the valves as the crank approaches this point 416., when the valves are closing. At the same time it will increase the leverage exerted upon the cranks 17 to open the valves when this ismost needed. Though,- as shown, the valves are hand operated, I intend controlling them vsinglyor in groups by an automatic governing-mechanism, such as is described in an application filed by me on April-7, 1903, Serial No.-151,'504.' 1 If a proper fluid-pressure be supplied to the outwardly from between them. action of this kind, whether carried on within a single compound casing or a series of sepajratecasings, it becomes of maximum importance to reduce the leakage of fluid-pressure This has passage 5, the active nozzles 7', after transforming aportion of the fluids energy'of pressure into energy of velocity, will deliver it in streams against the-first row of revolving vanes 41:, causing them to rapidly rotate. As

the fluid is delivered to the succeeding rows of nozzles, which increase in area to a calculated extent, fractions of its total pressure.

will be converted into velocity at each stage.

This velocity, which is due to the drop in pressure, will be totally absorbed by the moving vanes, so that they deliver to the succeeding row of nozzles only the remaining energy of pressure in the fluid, except at the last stages, when the vanes may be lengthened.

out and the pressure of the exhaust so rethem also its energy of reaction in expanding from thewheel-compartments not only with a View to economy, but because the turbine parts will be thrown out of proportion to the pressure and its efficiency affected, unless the calculated pressure at each stage should remain constant. With this object in view I interpose in the stuffing-boxes 23 and 24'of' the turbine-casing and in the central openings in the diaphragms of a compound turloine anannular pressure-reducing valve 25,

which surrounds the shaft and is adapted to move longitudinally of itself between collars or disks 26 in the stufling-boxes and wheels 3 in the turbine-casing, which serveas its seats. Referring now to the valves int-he turbine,

connection therewith while permitting of its longitudinal adjustment. It is not intended that the valve 25 should rotate, and it may therefore have a'vertically-disposed slot 29,

correspondin g in length with the valves play,

which is engaged by'a lug or, projection 30; but the valve may be permitted to rotate slowly, following the rotation of its seats. The ring 28 is preferably of an integral springpiece and may have, its lower facei. e., the

face toward thelow pressurecurved so as to form a rocking or ball-joint seat with the correspondinglycurved lower face 'of the groove 27, as shown more clearly in Fig. 10. The springs 31 (shown in this figure) may be In a cycle of duced that the fluid afterdelivering its 'energy of impact to the vanes will exert against used, if desired, to take up the shifting movementsof the valve and ring. When the ballfaced joint is used with the ring, the valve does not seat flush against the inner convex walls of'the flanged diaphragm-opening,but

is slightly-clear ofit, which, permits of the valve assuming larger angular variations to" compensate all ordinary changes of the relative positions of the rotating to the stationary parts caused by diiferences in expansion, eontraction, defection, wear, or defective adjustwith annular partitions or flanges 32, having grooves, packing-rings, and valves, as in the turbine, with theexception that the valves will be reversed to head toward the high pres-- The disks or collars 26' sure in the casing. correspond to the rotor-wheels in that they form the revolving seats for these valves, any desired number of which may be used. In the stuffing-box 24 the collar has a flange 33, which dips into a water-receptacle 34, forminga water-seal valve to prevent air entering the turbine when operated by steam and run condensing. opening 35 and discharged through an outlet 36.

The valves 25, which I use to control the leakageof pressure, are annular rings, either integral or in sections bolted together, which have circular longitudinally extending flanges 37, disposed around the upper or highpressure end of the valves, and flaring outwardly-disposed flanges 38, having a circumferential lip 39 on the lowpressure ends. For convenience in describing the action of the valve as applied to a compound turbine the pressure in the first wheel-compartment will be represented by A, that in the second by B, &c., and it will here be noted that the pressure of the whole compartment being the same it will be equal on both sides of each wheel and the end thrust will thus be reduced to a minimum.

\Vhen the turbine is in action, the pressure A in the discharging-compartment will be in excess of B in the receiving-compartment, which difference of pressure I use in connection with the valves 25 to create a third pressure within said valves, which I term the pressure of equilibrium. This pressure is maintained within the annular space or clearance between the valve and the shaft or the flanged hubs of the wheels which inclose the shaft, and this space may be enlarged for the purpose of increasing the area of this pressure and making its effect on the valve more positive by forming a chamber in the inner periphery of said valve, as in Fig. 10, and

\Vater is admitted through an and the lip 39, communicating with the lowpressure eompartment,-and it is my intention to so shape the valve that, sensitive to the diflerent pressures between which it acts, it will automatically adjust itself to its seats,

so as to regulate the openings a and b, with a view to controlling and maintaining the pressure of equilibrium, which is intermediate the pressures above and below the valve.

According to Fig. 8, where an annular valve of the plain type is shown, this pressure of equilibrium cannot exist, because the pressure A, passing the opening a, presses the valve down with a pressure per square inch equal to the dilference between the pressures A and B, and though there will be a pressure within the valve it will remain whollyin one direction, since the valve is rectangular in cross-section and can have no .lifting effect on the valve to counteract the downward thrust of the pressure A, which presses it hard against the face of the lower wheel. This will stop all leakage; but the speed of rotation of the wheels in these turbines is so great that such a bearing would be impractical on account of friction. Therefore according to my preferred form I make provision for a small leakage to occur at this valve, which I utilize for several purposes, of which the most important is the maintenance of the pressure of equilibrium. Referring now to Fig. 9, it will be seen that the pressure A enters the valve-chamber through a and passing under the valves flange 38 counteracts or equalizes the "alves end thrust; but the lip 39 will still be pressed against the lower wheel by the pressure B on top of the projecting flange 38. This difliculty is positively removed by extending this flange, as shown in Figs. 5, 10, and 11, for we now have the pressure A passing around the valve and under the flange, and when it exceeds in the recessed area under the flange the pressure of B upon the flange in addition to the weight of the valve the latter will rise.

When this occurs, the flange 37 approaches the upper wheel, wiredrawing the opening a and reducing the pressure A entering the valve-chamber from the high-pressure compartment, while simultaneously the opening bis eifected and pressure escapes from the valve-chamber into the pressure B in the lowpressure chamber. This occurs until a pressure of equilibrium is reached in the valvechamber, when the valve remains at rest, and the pressure is maintained by the gradual leakage around the valve. This small leak is not only of such a character that it can be readily calculated, but it also serves the purpose of lubrication by maintaining a thin film of lubricated steam or other elastic fluid passing between the flanges 37 39 and their rotating seats. It also prevents the accumulation of water, which would cause great friction between the stationary and rapidly-rotating parts. Thus instead of endeavoring to stop the leakage entirely it is my intention to control or regulate it within limits, so that it may be calculated and provided for in the turbine construction.

The quantity of elastic fluid required to maintain this equilibrium pressure being determined, partly by the area of the flange 38, the area of the opening I), and'the difference in pressures above and below the valve, it is evident that the parts may be so designed that the valve will touch'the upper wheel with any desired degree of pressure less than the difference between the pressures A and B. In the same manner this pressure can be so adjusted that the frictional heat caused by the contact of the two surfaces will not be so great that it cannot be readily conducted away through the fluid and the mechanism.

The valve'may also be caused to suspend itself in equilibrium between the moving wheels or disks without having contact with either or to approach the upper as closely as may be desired and operate thus with a thin annular film of lubricated fluid separating it from the wheel-face. The thickness of this film may be regulated so that only enough fluid to keep its faces 37 and 39 lubricated v and to cause sufficient circulation to prevent condensation within the turbine will be allowed to pass.

As'applied to a' stage-expansion turbine comprising a series of simple turbines in separate casings, my improved'valves will be lo-' c'ated in the stuffing-boxes of the several casings, which boxes may ,be common to adjoining casings, to which the fluid is successively conducted through conduits.

. may be in the form of straight nozzles with parallel sides, or they may converge toward their discharge ends, or they may be of the expansion type, diverging toward'their discharge ends; but whatever the shape used they will have rounded entrances to keep their capacity efficiency high; They may be' used with or without valves, and where valves are used they will be shaped to form'therounded entrances to" the passages wh'enopen.

"The passages will be designedwith a viewto keeping the proper pressure constantly the same at the different stages during the turbine action, and theywill be required to transform' to velocity only' such portion of the pressure aswill be absorbed by the first succeeding row of vanes; The type of thenozzle to be used depends'on the percentage of the stage pressure which it must convertinto velocity, and this 'is determined by comparing the total pressure of the discharging with that of the receiving compartment. Thus if the discharge-compartment has a pressure of one hundred pounds per square inch and the receiving-compartment eighty pounds there will be a twenty-per-cen t. drop, in which case I will use either the straight or the converging nozzle, according to the shape of thereceiving buckets orvanes, and with either of these nozzles I can obtain all the velocity due to the twenty-per-cent. drop in pressure. Also by maintaining the receiving-compartments pressure at eighty pounds, which is the pressure of efliux of the nozzle, the stream will have no tendency to further expand after delivery from the nozzle, making its energy easy to transform into motion in the vanes. In cases when the drop is greater than fortytwo per cent. of the pressure in the discharging-compartment I will form the nozzles to diverge toward their discharge ends and at a Y sure thus transformed may be converted'int'o velocity, and there will thus be no further expansion of the fluid after it leaves the nozzle. In places where the final pressure is high'I may use the straight nozzle for in'jecting the'fluid into the last row of vanes, and

in such cases where the drop is greater than forty-two per cent. I will shape the vanes to form a'series of deep receptacles, so that they will absorb all the velocity of impact and in discharging the remaining pressure will absorb therefrom the energy of its lineal reaction.

Obviously the'application of my pressure reducing valve to control the leakage between different pressures, whether atmospheric or otherwise, makes its field of usefulness-independent of any specific form of turbine, though in the application shown the construction and control of the'fluid-passag'es are especially adapted to cooperate with the valve in maintaining constant the stage pressures. By the expression compartment?- I mean achamber' within which a wheel rotates,

whether it be separate from or combined with similar chambersin the same or casings.

f Having thus described my invention, what diiferent I claim as new, and desire to secureby Letters tating elements which form seats for said rings and between which they are automatically adjustable.

In a compound elastic-fluid turbine having a plurality of diaphragm-partiti011s forming separate wheel-compartments, the combination with a plurality of wheels intermediate the partitions, of means carried by said partitions and automatically adjustable between said wheels revolving surfaces to control the leakage between compartments.

4. In an elastic-fluid turbine operating by stage expansion, a series of separate compartments within which different pressures are maintained, of an automatic pressure-reduc ing valve to govern the leakage between compartments.

5. In an elastic-fluid turbine operating by stage expansion, a plurality of separate wheel-compartments, a shaft, wheels thereon which revolve within said compartments, and means, automatically sensitive to the difierencein pressures between the compartments, which maintain between the partitions and the shaft pressures intermediate those of the communicating compartments which control said means.

6. In an elastic-fluid turbine, avalve placed at a point of leakage between diiferent pressures whether atmospheric or otherwise, a seat therefor, the said valve being adapted to maintain within itself a pressure intermediate those between which it operates, and to be actuated and controlled by said intermediate pressure to regulate the leakage at that point.

7. In a compound elastic-fluid turbine operating by stage expansion, a series of partitions forming compartments wherein diflerent pressures are maintained, and a series of movable rings which automatically maintain between said'compartments a series of intermediate pressures.

S. In an elastic-fluid turbine, a flanged ring-valve adapted to act at a point of leakage near the shaft between dilferent pressures, said valve having a transverse flange in its low-pressure end, and a seat therefor, between which and said flange the higher pressure has access to automatically actuate the valve.

9. I11 an elastic-fluid turbine, a ring-valve adapted to act at a point of leakage between compartments wherein different pressures are maintained, a seat for said valve in each compartment, a flange on said valve disposed within each compartment which are acted on by the different pressures and proportioned to control the pressure-reducing action of the valve.

10. In a turbine of the class described, a plurality of wheel-compartments having dif ferent pressures, wheels, annular rings interposed between compartments, said rings having outwardly-projecting flanges around their low-pressure ends and a flange around their high pressure end, and means to support said ring-pressure tight while permitting of its endwise adjustment between the faces of the wheels which form its seats.

11. In a turbine of the class describcd,rings loosely surrounding the shaft and placed at points of leakage between different pressures, whether atmospheric or otherwise, revolving disks carried by said shaft between which said rings are adjustably suspended, said rings being sensitive to the diiference of the pressures between which they operate and so proportioned relative thereto that they are automatically maintained in a position relative to said disks to govern the said leakage.

12. In an elastic fluid turbine, stationary diaphragm partitions forming wheel compartments wherein different fluid pressures are maintained, a shaft, rotor-wheels thereon having concave-convex vanes, and a movable annular flanged packing-ring between compartments which leaves a clearance around said shaft.

13. In a turbine of the class described having wheel-compartments wherein diiferent fluid-pressures are maintained, a shaft, rotorwheels thereon, an annular packing-ring between compartments adapted to act as a pressurereducing valve and maintain in its interior a third pressure, which third pressure is different from the compartment pressures and suspends said valve between its moving seats.

14. In a turbine of the class described having separate compartments wherein different pressures are maintained, rotating elements therein, nozzle-passages connecting said compartments, and annular valves between compartments and sensitive to the differences in pressures therein by which they are automatically held to their seats with a pressure less than said differential between which they operate.

15. In an elastic-fluid turbine, an annular valve adapted to act at a point of leakage around the shaft between different pressures, a stationary support for said valve, a ballfaced groove in said support, a packing-ring around said valve having a ball-faced bearing end seated in said groove.

16. In an elastic-fluid turbine acting to expand the fluid-pressure in stages, stationary partitions'forming compartments and rotating elements therein, in combination with means for maintaining predetermined pressures in the several compartments comprising fluid-passages in said partitions, separate valves in each passage, and means to automatically regulate the leakage of pressure between compartments.

17. In an elastic-fluid turbine operating by stage expansion, a series of wheel-compartments, wheels therein, nozzlepassages between compartments designed to convert equal quantities of the total pressure into velocity at each stage, and means cooperating therewith to maintain the pressure in each compartment equal to the pressure of the fiuid-stream-delivered thereto by regulating the leakage between compartments.

18. In an elastic-fluid turbine of the class described, circular rows of fluid-passages alternating with rows of revolving vanes,valves in said passages, operating-stems for said valves, links connecting said stems across the rows and an operating-lever connected'to said links and in alinement therewith when the valves are'closed.

19. In an elastic-fluid turbine operating by stage expansion, a series of wheel-compartments, wheelshaving peripheral-vanes revolving in said compartments, nozzle-passages between said compartments which direct the fluid-streams against said vanes, valves controlling theadmission of pressure to said nozzles, means to simultaneously open or close the same number of valves in each succeeding row of nozzles, and automatic means to govern the leakage between compartments.

20. Inan elastic-fluid turbine, a series of diaphragm-partitions dividing it into several compartments, wheels having peripheral vanes revolving in said compartments,nozzles in said partitions which effect a predetermined reduction in the pressure of the elastic fluid which is absorbed by a succeeding row of vanes to which it is delivered, valves in said nozzles, and automatic means to regulate the leakage between compartments.

21. I11 an elastic-fluid turbine wherein pressure is reduced in stages and directed by successive nozzle-passages against intermediate rows of vanes, a plurality of rows of nozzles, part of which expand the fluid pressure'only lineally, while the other rows expand it both to succeed each other in the direction of the flow of the fluid, valves for said nozzles which when open form the rounded entrances to said nozzles, stems for said valves which project radially from the casing, cranks on said stems, and links connecting said cranks together in the line of the fluids flow.

In testimony whereof I affix my signature in presence of two witnesses.

, JAMES XVI'LKINSON. \Vitnesses H. B. URQUHART, H. F. WILsEN. 

